WO2020129012A1 - Assembly of at least two brake pads and at least one spring - Google Patents

Assembly of at least two brake pads and at least one spring Download PDF

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Publication number
WO2020129012A1
WO2020129012A1 PCT/IB2019/061201 IB2019061201W WO2020129012A1 WO 2020129012 A1 WO2020129012 A1 WO 2020129012A1 IB 2019061201 W IB2019061201 W IB 2019061201W WO 2020129012 A1 WO2020129012 A1 WO 2020129012A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
pads
coupling
edge
disc
Prior art date
Application number
PCT/IB2019/061201
Other languages
French (fr)
Inventor
Mauro Mambretti
Andrea MECOCCI
Alberto PENDESINI
Giuseppe SPIGAPIENA
Alberto Bosis
Original Assignee
Freni Brembo S.P.A.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from IT102018000020527A external-priority patent/IT201800020527A1/en
Priority claimed from IT102019000023940A external-priority patent/IT201900023940A1/en
Application filed by Freni Brembo S.P.A. filed Critical Freni Brembo S.P.A.
Priority to US17/416,062 priority Critical patent/US11852207B2/en
Priority to EP19836587.6A priority patent/EP3899306A1/en
Priority to CN201980084775.2A priority patent/CN113195920B/en
Priority to JP2021536008A priority patent/JP2022515189A/en
Publication of WO2020129012A1 publication Critical patent/WO2020129012A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0972—Resilient means interposed between pads and supporting members or other brake parts transmitting brake reaction force, e.g. elements interposed between torque support plate and pad
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0975—Springs made from wire
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/0006—Noise or vibration control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0977—Springs made from sheet metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F16D2055/0029—Retraction devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/02—Release mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/005—Components of axially engaging brakes not otherwise provided for
    • F16D65/0068—Brake calipers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/12—Discs; Drums for disc brakes

Definitions

  • the present invention relates to an assembly comprising at least two pads and at least one spring for elastically retaining and biasing the pads in a disc brake caliper, as well as to a caliper comprising such an assembly and a disc brake equipped with such an assembly.
  • Disc brake springs which consist of a central portion and two end portions, in which the end portions rest against the pads so as to bias the pads elastically away from each other to ensure a separation of the pads from the brake disc after each braking operation.
  • the known springs are kept in their operating position by fixing the central portion of the springs to the caliper.
  • the springs of the prior art generally comprise one or more connecting appendages, formed at the central portion of the expansion spring, adapted to connect the springs to the caliper at coupling portions formed on the caliper.
  • document DE102017204696 shows a solution of this type.
  • the springs of the prior art usually abut against an apical portion of the pads, and therefore transmit a direct distancing force to the pads at the top of the pads, top which is understood as the radially outer edge with respect to the rotation axis of the brake disc.
  • each axis parallel to the brake disc rotation axis is named axial direction A-A
  • each direct axis orthogonal to the axial direction and incident with the brake disc rotation axis is named radial direction R-R
  • each direction orthogonal to both the axial and radial direction is named circumferential direction C-C which punctually forms a tangential direction T-T.
  • the present invention relates to a solution which keeps the spring away from the disc under all conditions of use, i.e. under all conditions of brake pad wear.
  • the present invention also relates to a solution which keeps the pads substantially with their friction surfaces parallel to the friction surfaces of the brake disc that they face.
  • an assembly comprising two disc brake pads and at least one spring configured to bias the pads elastically according to claim 1 , by a caliper according to claim 10, and by a disc brake according to claim 13, as well as by a method of biasing two opposite pads constantly and elastically according to claim 14.
  • the dependent claims relate to advantageous and preferred embodiments.
  • the spring is constantly connected to the pads as the wear varies, i.e. according to the variation of the distance between the two pads 6, and therefore of the distance between the two portions of the spring attachment to the pads. It is also ensured that the forces applied by the spring on the plate are only axial (perpendicular to the plane of symmetry in the figures indicated with reference numeral 16) and that no torques are applied which could cause the rotation of the plate itself.
  • the spring system on the plate is configured as a hinge.
  • the inclinations of the spring arms are such that the spring is parallel to the surface of the disc under maximum wear conditions, thus avoiding contact of the spring with the disc.
  • the shape of the second connection 24 ensures that the spring can be taken to the maximum wear condition with the sliding connection sections on the inner upper edge and the upper surface of the plate coupling seat.
  • the spring is prevented from slipping out of the caliper in a radial direction (parallel to the symmetry axis 16) under the condition of maximum wear of the pads. Flowever, this hook does not work to attach the plate externally, remaining facing the lower edge of the plate itself and mostly not in contact under conditions of normal use.
  • FIG. 1 is a perspective view of a disc brake according to an embodiment of the invention.
  • FIG. 1 is a further perspective view of the disc brake in figure 1 ;
  • - figure 3 is a radial section view (with respect to a rotation axis of a disc brake) of the disc brake in figure 1 under non-worn pad condition,
  • figure 4 is a further radial section view of the disc brake in figure 1 , under worn pad condition;
  • FIG. 5 is a cross-section view (with respect to a rotation axis of a disc brake) of the disc brake in figure 1 ;
  • figure 6 is a front view of a pad of the disc brake in figure 1 ;
  • figure 7 is a perspective view of the pad in figure 6;
  • figure 8 is a front view of a spring of the disc brake in figure 1 ;
  • figure 9 is a perspective view of the spring in figure 8.
  • FIG. 10 shows a perspective side of a brake caliper according to a further embodiment
  • figure 1 1 is an axonometric view of a detail of an assembly of pads facing each other and an interposed spring associated therewith;
  • FIG. 12 is a front view of a detail of a brake pad according to a different embodiment, in which the detail of the coupling position of the brake pad to the spring is highlighted;
  • figure 13 is a top view of the detail in figure 12;
  • FIG. 14 shows an axonometric view of a spring according to a further embodiment
  • figure 15 is a front view of the spring in figure 14;
  • FIG. 19 to 22 diagrammatically show a spring connected to a plate coupling portion in which four different pad positions are illustrated, as a function of four different conditions of wear of the friction material not shown, to highlight the actions which are exchanged by the spring to the plate coupling portion;
  • FIG. 23 diagrammatically shows a spring associated with two opposite plate coupling portions, in which the actions of the spring are broken down in radial and axial directions to show how the radial actions substantially compensate each other and the resulting are axial actions which constantly and elastically bias the pads as they move away from the disc.
  • a disc brake in particular for use on motor vehicles, is globally indicated by reference numeral 1 .
  • it is a disc brake of the floating caliper type.
  • the invention is also applicable to brakes with fixed calipers.
  • the disc brake 1 comprises a caliper 2 and a brake disc 3, in which the brake disc 3 defines a rotation axis 10.
  • the caliper 2 is arranged straddling the brake disc 3 and can be fixed to a bracket 4 by means of a sliding support (e.g. fig. 1 -2).
  • the bracket 4 is fixed to a vehicle suspension, while the brake disc 3, provided with an annular braking band 5, can be connected to the wheel hub of the vehicle (not shown).
  • the brake disc 1 comprises an assembly 100, wherein the assembly 100 comprises at least two pads 6 having a support plate 7 and a friction material coating 8, each of said at least two pads 6 is adapted to be accommodated in an appropriate pocket
  • each of said at least two pads 6 can be positioned on a side of a brake disc 3 of a disc brake 5 (e.g. fig. 3-5).
  • the pads 6 can be displaced mainly in axial direction (parallel to the rotation axis
  • thrust means e.g. such as one or more hydraulic cylinder-piston units 1 1 arranged in the caliper 2, so as to clamp, via the friction material 8, a sector of the braking band 5, the surface and shape of which corresponds to those of the friction lining 8.
  • the support plate 7 of the pads 6 has a substantially rectangular shape and forms two ears 12 protruding outwards from the support plate 7.
  • Each one of the two ears 12 forms an abutment wall 14 adapted to be inserted in the pockets 9 of the caliper 2.
  • the abutment wall 14 has an angular shape, forming a first abutment wall 14’ and a second abutment wall 14’ adapted to abut against a plate mounted on two different surfaces of a pocket 9 of the caliper 2 (e.g. fig. 5-7).
  • each of the ears 12 forms a coupling seat 13.
  • the assembly 100 further comprises at least one spring 15 shaped to be positioned straddling the brake disc 3, and which applies an elastic preload on the pads 6 so as to bias the pads 6 elastically away from the brake disc 3.
  • the at least one spring 15 may perform the further function of stopping the pads 6 elastically in the pockets 9 so as to reduce the onset of vibrations and noise due to movements of the pads with respect to the caliper 2.
  • the spring 15 is configured so as to be directly connected only to the pads 6 (fig. 3-5). Therefore, the spring 15 is not constrained by any other disc brake component 1 except for the pads 6.
  • such a configuration increases the assembly flexibility of the at least one spring 15 to the disc brake 1 because the at least one spring 15 is connected exclusively to the pads 6, and thus may be implemented indifferently to various disc brakes 1 and various calipers 2, with no need to adapt such disc brakes 1 or such calipers 2 to the spring 15 or vice versa.
  • two springs 15 are arranged straddling the brake disc 3, so as to apply an elastic preload on the pads 6.
  • each of the two springs 15 is connected to the ear 12 of a first pad 6 and to the corresponding opposite ear 12 of the other pad 6, respectively.
  • At least one spring 15 is substantially shaped as an inverted“U” (fig. 8-9).
  • the at least one spring 15 defines a symmetry plane 16 (geometric, not material) which is transverse to the rotation axis 10 of the brake disc 3 when at least one spring 15 is mounted in the operating position.
  • the at least one spring 15 consists of two coupling portions or spring arms 17 and of a bridge portion 18 interposed between the two coupling portions or spring arms 17.
  • the two coupling portions or spring arms 17 are configured to couple to a respective ear 12 of the two pads 6 and said two coupling portions or spring arms 17 are symmetrical with respect to the symmetry plane 16.
  • the spring 15 is deformed elastically (in particular, by accumulating elastic energy) by a relative movement of the coupling portions or spring arms 17, moved by the respective pads 6, with respect to the bridge portion 18.
  • each of the two coupling portions or spring arms 17 is connected to the bridge portion 18 by means of a first connector 19, wherein the first connector 19 is shaped as a loop or arc of circumference.
  • such a shape of the first connector 19 ensures that the elastic return force of the spring 15 (caused by the elastic deformation of the spring 15 by the action of the pads 6) is incremental as the wear of the pads 6 varies, i.e. as the distance between the two coupling pads 6 (and therefore the distance between the two coupling portions or spring arms 17 attached to the pads 6).
  • each of the coupling portions or spring arms 17 of the spring 15 is substantially“Z”-shaped.
  • each of the coupling portions or spring arms 17 consists of a first diagonal portion 21” and a second diagonal portion 21”, which are substantially parallel to each other, between which a return portion 22, which is substantially transversal to the two diagonal portions 21”, 21”, is interposed.
  • the return portion 22 is configured so as to lie on a respective coupling seat 13 of the ears 12.
  • such configuration of the return portion 22 guarantees that the spring 15 is constantly connected to the pads 6 when the wear of the pads 6 varies, i.e. with the distance between the two pads 6 (and therefore the distance between the two coupling portions or spring arms 17 coupled to the pads 6), and in particular when the pads 6 are new and the spring is very open (fig. 3-4).
  • first diagonal portion 2T of each of the coupling portions or spring arms 17 is connected at a first end thereof to the return portion 22 by means of a second connector 24, wherein the second connector 24 is shaped as a loop or arc of circumference.
  • such a shape of the second connector 24 further ensures that the elastic return force of the spring 15 (caused by the elastic deformation of the spring 15 by the action of the pads 6) is incremental as the wear of the pads 6 varies, i.e. with the distance between the two coupling pads 6 (and therefore the distance between the two coupling portions or spring arms 17 attached to the pads 6) when the disc brake 1 is not actuated.
  • a second end of the diagonal portion 2T forms a hook-shaped end portion 23.
  • such a hooked end portion 23 further guarantees a correct and stable connection of the spring 15 to the ears 12 of the pads 6.
  • the spring 15 is configured so that, in the working position, the coupling portions or spring arms 17 are interposed between the pads 6 and the brake disc 3.
  • the spring 15 is of the leaf type.
  • the spring 15 is formed in a single strip shaped steel piece shaped so as to display only curvatures about axes which are substantially parallel to one another and substantially parallel to the symmetry plane 16 of the spring 15.
  • sheet material e.g. spring steel
  • a caliper 2 comprises the assembly 100 described above.
  • the caliper 2 is of the“floating” type.
  • a disc brake 1 comprises the assembly 100 described above and the caliper 2 described above.
  • an assembly 100 comprises at least two pads 6 having a support plate 7 and a friction material lining 8.
  • Each of said at least two pads 6 is adapted to be accommodated in a pocket 9 of a caliper 2 so that each of said at least two pads 6 can be positioned on a side of a brake disc 3 of a disc brake 1 facing opposite braking surfaces 36.
  • Said brake disc 3 is a rotor adapted to rotate about a rotation axis 10 which defines an axial direction A-A, parallel to said rotation axis 10, a radial direction R-R, orthogonal to said rotation axis 10, and a circumferential direction C-C orthogonal to said axial A-A and radial R-R directions and a tangential direction T-T orthogonal to a radial R-R and circumferential C-C direction at their point of intersection.
  • Said assembly 100 further comprises at least one spring 15, shaped to be arranged straddling the disc brake 3.
  • Said spring 15 applies an elastic bias on the pads 6 so as to bias the pads 6 elastically away from the brake disc 3.
  • Said at least one spring 15 is configured to be directly connected only to the pads 6.
  • Said support plate 7 comprises at least one plate coupling portion 37.
  • said plate coupling portion 37 comprises:
  • Said inner upper edge 26 continues on a direct upper surface 27 according to an axial direction A-A parallel to said disc rotation axis 10, thus forming an upper spring coupling plate portion edge 29.
  • said spring 15 is always in contact exclusively with:
  • said spring 15 is a wire spring made in one piece.
  • said spring 15 is a wire spring having a circular cross-section.
  • said spring 15 is a wire spring made in one piece and said spring 15 is always in contact exclusively with a point or a line of said inner lower edge 25 and said upper spring-coupling plate portion edge 29.
  • said inner upper edge 26 is radially arranged on the side opposite to said inner lower edge 25.
  • Said inner upper edge 26 continues on a direct upper surface 27 according to an axial direction A-A parallel to said disc rotation axis 10.
  • Said upper surface 27 continues on an outer upper edge 28 adapted to be rotated in the opposite direction to the brake disc 3.
  • Said spring 15 is always in contact with said upper inner edge 26 or said upper surface 27 or said upper outer edge 28.
  • said spring 15 avoids resting on anything else but said at least two pads 6, thus avoiding the connection to said caliper 2 for relieving all or part of the elastic reaction thereon.
  • said assembly 100 comprises two springs 15 adapted to be arranged straddling the brake disc 3, so as to bias the pads 6 elastically and wherein both said two springs 15 are configured to be directly connected only to the pads 6.
  • said two springs 15 are disconnected at opposite sides of said two pads 6.
  • the support plate 7 of the pads 6 is substantially rectangular in shape, said support plate 7 forms two ears 12 which extend towards the outside of the support plate 7 in circumferential direction C-C.
  • said at least one spring 15 cooperates with at least one of said ears 12.
  • each of the two ears 12 forms:
  • an abutment wall 14 adapted to be abuttingly inserted into the pockets 9 of the caliper 2, wherein the abutment wall 14 is angular in shape, thus forming a first abutment wall 14’ and a second abutment wall 14” adapted to abut against metal sheets mounted to two different surfaces of a pocket 9 of the caliper 2;
  • each of the two springs 15 is connected to the ear 12 of a first pad 6 and to the ear 12 of the other pad 6, respectively, either directly or indirectly facing said first pad ear 12.
  • said at least one plate coupling portion 37 comprises said upper spring-coupling plate portion edge 29, one inner pad coupling portion side 30, adapted to face either directly or indirectly said brake disc 3, and a lower spring-coupling plate portion edge 30 comprising said inner lower edge 25 which continues on a lower surface 31 directed according to an axial direction A-A parallel to said disc rotation axis 10.
  • said upper spring-coupling plate portion edge 29 comprises an upper spring seat edge 32 shaped to fit intimately with a coupling portion or spring arms 17.
  • said lower spring-coupling plate portion edge 31 comprises a lower spring seat edge 34 shaped to fit intimately with a coupling portion or spring arms 17.
  • said inner pad coupling portion side 30 comprises an inner spring seat side 33 shaped to fit intimately with a coupling portion or spring arms 17.
  • the at least one spring 15 is substantially inverted“U”-shaped, and said at least one spring 15 defines a symmetry plane 16.
  • the at least one spring 15 comprises two coupling portions or spring arms 17 and of a bridge portion 18, said bridge portion 18 being interposed between the two coupling portions or spring arms 17.
  • said coupling portions or spring arms 17 are configured to be coupled to a respective ear 12 of the two pads 6.
  • said two coupling portions or spring arms 17 are symmetrical with respect to the symmetry plane 16.
  • the spring 15 is elastically deformable by means of a relative movement of the coupling portions or spring arms 17, said coupling portions or spring arms 17 being movable by the respective pads 6, with respect to the bridge portion 18.
  • each of the two coupling portions or spring arms 17 is connected to the bridge portion 18 by means of a first connector 19, wherein said first connector 19 is shaped as a loop or arc of circumference.
  • said first connector 19 is spiral-shaped.
  • said first connection 19 is spiral-shaped with at least one first connection loop 35 forming an angle of at least 360 DEG.
  • each of the coupling portions or spring arms 17 of the spring 15 is substantially“Z”-shaped, and each of the coupling portions or spring arms 17 comprises:
  • the first diagonal portion 21’ and the second diagonal portion 21” are substantially parallel to each other, and the return portion 22 is interposed between the first diagonal portion 21’ and the second diagonal portion 21”, said return portion being substantially transverse to the first diagonal portion 21’ and to the second diagonal portion 21”.
  • the return portion 22 is configured so as to lie on a respective coupling seat 13 of the ears 12.
  • the first diagonal portion 21’ of each of the coupling portions or spring arms 17 is connected at a first end thereof to the return portion 22 by means of a second connector 24, wherein the second connector 24 is shaped as a loop or arc of circumference.
  • a second end of the diagonal portion 21’ forms a hook-shaped end portion 23.
  • the spring 15 is configured so that, in the working position, the coupling portions or spring arms 17 are interposed between the pads 6 and the brake disc 3.
  • the spring 15 is of the wire type.
  • the spring 15 is a spring leaf.
  • the spring 15 is formed in a single strip shaped steel piece shaped so as to display only curvatures about axes which are substantially parallel to one another and substantially parallel to the symmetry plane 16 of the spring 15.
  • the present invention further relates to a caliper 2 comprising an assembly 100, said assembly 100 comprising at least two pads 6 and at least one spring 15 according to any one of the embodiments described above.
  • the at least one spring 15 is configured to perform the further function of stopping the pads 6 elastically in the pockets 9 so as to reduce the onset of vibrations and noise due to movements of the pads with respect to the caliper 2.
  • said caliper body 2 is of the“floating” type.
  • the present invention further relates to a disc brake 1 comprising:
  • the present invention further relates to a method for biasing two facing brake pads 6 constantly and elastically by means of a spring 15, wherein there are provided the steps of:
  • Second connector 25 Inner lower edge

Abstract

An assembly (100) comprising: • - at least two pads (6) having a support plate (7) and a friction material coating (8), each of said at least two pads (6) being adapted to be accommodated in a pocket of a caliper so that each of said at least two pads (6) can be positioned on a side of a brake disc (3) of a disc brake facing opposite braking surfaces; said brake disc (3) being a rotor adapted to rotate about a rotation axis • - at least one spring (15), shaped to be arranged straddling the disc brake (3), wherein said spring (15) applies an elastic bias on the pads (6) so as to bias the pads (6) elastically away from the brake disc (3); wherein said at least one spring (15) is configured to be directly connected only to the pads (6); said support plate (7) comprises at least one plate coupling portion (37), wherein, in a section of said plate coupling portion (37) on a plane containing the axial direction and the radial direction, said plate coupling portion (37) comprises: • - an inner lower edge (25), adapted to face the brake disc (3) in the radially inward direction or towards the disc rotation axis; • - an inner upper edge (26), adapted to face the brake disc (3) in the radially outward direction or opposite to the disc rotation axis; • - said inner upper edge (26) continues on a direct upper surface (27) according to an axial direction parallel to said disc rotation axis, thus forming an upper spring-coupling plate portion edge; and wherein said spring (15) is always in contact exclusively with: • - said inner lower edge (25) and • - said upper spring-coupling plate portion edge.

Description

“Assembly of at least two brake pads and at least one spring”
[0001] FIELD OF THE INVENTION
[0002] The present invention relates to an assembly comprising at least two pads and at least one spring for elastically retaining and biasing the pads in a disc brake caliper, as well as to a caliper comprising such an assembly and a disc brake equipped with such an assembly.
[0003] BACKGROUND ART
[0004] Disc brake springs are known which consist of a central portion and two end portions, in which the end portions rest against the pads so as to bias the pads elastically away from each other to ensure a separation of the pads from the brake disc after each braking operation.
[0005] The known springs are thus used to obtain a three-fold action:
[0006] - to reduce the vibrations of the pads;
[0007] - to distance the pads from the brake disc in order to reduce or eliminate a residual braking torque (residual torque) due to undesired contacts between the pads and the brake disc with the brake deactivated;
[0008] - to obtain uniform wear of the friction linings of the pads.
[0009] Usually, the known springs are kept in their operating position by fixing the central portion of the springs to the caliper.
[0010] In particular, the springs of the prior art generally comprise one or more connecting appendages, formed at the central portion of the expansion spring, adapted to connect the springs to the caliper at coupling portions formed on the caliper.
[0011] For example, document DE102017204696 shows a solution of this type.
[0012] Such a fixing requires to design the springs specifically for the caliper for which they are intended to be connected.
[0013] Moreover, these known solutions, by relieving the reaction of the elastic bias applied on the pads at least partially in the caliper body, can determine an unbalanced, or in any case not symmetrical, elastic action on opposite pads, thus also generating, under particular conditions, uneven pad displacement and therefore at least initially uneven applications of the braking actions applied on the brake disc, at least at the beginning of the braking action of the vehicle.
[0014] Furthermore, such a configuration requires to allocate a portion of the caliper to allow the coupling portion to connect the springs to the caliper.
[0015] Moreover, the springs of the prior art usually abut against an apical portion of the pads, and therefore transmit a direct distancing force to the pads at the top of the pads, top which is understood as the radially outer edge with respect to the rotation axis of the brake disc.
[0016] For the sake of convenience, in brake systems, reference is made to the rotation axis of the brake disc, albeit virtual in the case of components removed from the vehicle. Each axis parallel to the brake disc rotation axis is named axial direction A-A, each direct axis orthogonal to the axial direction and incident with the brake disc rotation axis is named radial direction R-R and each direction orthogonal to both the axial and radial direction is named circumferential direction C-C which punctually forms a tangential direction T-T.
[0017] The action of the spring on the outer radial edge of the pad causes uneven and sometimes incomplete detachment between brake pads and brake disc, which determines a residual torque, unplanned pad positioning and orientation and uneven pad wear. However, this elastic action mainly at the top of the pads tends to position the pad itself not facing parallel to the braking surface of the disc and not perfectly facing the rear or plate surface of the thrust means, typically hydraulic pistons, thus causing an initial transient settling of the pad at each start of braking action and sometimes a non-optimal settling of the pad to the brake disc or piston which applies the braking thrust.
[0018] Therefore, in the sector, the need is felt for a brake pad and spring assembly solution which distances them away from the brake disc capable of applying an elastic bias with direct resultant in a direction parallel to the direction of the brake disc rotation axis.
[0019] In particular, the need is felt to prevent the spring from relieving its elastic action or reaction also on the clamp body, as for example shown in US 2014/124306 A1 and US6719105B1 by Kelsey-Hayes Company.
[0020] In document JP 2012 189188 by AKEBONO BRAKE IND., in particular, in embodiment shown in figure 12 (A and B), the spring moves the pads away from the disc resting it against the upper surface of the pad plates and elastically biases the edge between the plate and the friction material with the end of one of its arms placed radially. A similar solution is shown in JP2012072830 A, WO 02/33282 and US 2018/023645 A1. However, these solutions do not guarantee a direct action of the spring substantially only in the axial direction.
[0021] In document DE 10 2017 222639 A1 by CONTINENTAL TEVES AG & CO OHG, the spring connects to the upper surface of plate ears and embraces the lower surface and the edges of these ears. In this solution, in order to embrace the outer, inner and lower surfaces of the lower edge of the plate ear with the objective of keeping the pad vertical, the spring is closed as a box on three sides about the lower edge of the plate and is forced to prevent a consequent rotation of the pad caused by actions having different directions in addition to the axial one to couple the upper edge of the ear of the plate with a snap-coupling (indicated by reference numeral 26), holding the plate in radial direction. A similar solution is known from US2004104086 A1 . These solutions, besides being very complex, do not guarantee a substantially axial spring action.
[0022] OBJECT OF THE PRESENT INVENTION
[0023] It is one of the main objects of the present invention to provide a solution and a method which allows the biasing of brake pads substantially and mainly with a direct resultant in an axial direction.
[0024] At the same time, the present invention relates to a solution which keeps the spring away from the disc under all conditions of use, i.e. under all conditions of brake pad wear.
[0025] At the same time, the present invention also relates to a solution which keeps the pads substantially with their friction surfaces parallel to the friction surfaces of the brake disc that they face.
[0026] It is a further object of the present invention to provide an improved pad spring and disc brake, having features which increase the flexibility of mounting springs to the disc brake, make the spring independent from the shape of the caliper body, reduce the size of the spring inside the caliper, and minimize the residual torque.
[0027] It is a further object of the present invention to provide an improved pad spring and disc brake, such as to improve, in the most barycentric sense, at least in a radial direction, the elastic action applied by the spring.
[0028] It is a further object of the present invention to provide an improved pad spring and a disc brake, such to balance the elastic actions applied on the two opposite pads.
[0029] SOLUTION
[0030] These and other objects are achieved by an assembly comprising two disc brake pads and at least one spring configured to bias the pads elastically according to claim 1 , by a caliper according to claim 10, and by a disc brake according to claim 13, as well as by a method of biasing two opposite pads constantly and elastically according to claim 14. The dependent claims relate to advantageous and preferred embodiments.
[0001] By virtue of the suggested solutions, it is possible to bias the brake pads constantly and elastically facing the brake pads with an elastic bias action axially as direct as possible, thus avoiding to bias the pads with the spring by means of actions which a priori will certainly lead to angular actions or torques which can bias the correct position of the pads facing the disc as much as possible and with the friction surfaces of the friction material as parallel as possible to the friction surfaces of the brake disc.
[0002] Furthermore, by virtue of the suggested solutions, it is possible to keep the spring away from the disc even when the pads are under maximum wear conditions.
[0003] By virtue of the expected contact between the spring and the pad plates in their lower inner edge is limited to a point, or a line, allowing a better adjustment of the direction of action between the spring and the pad plate.
[0004] In further detail, by virtue of the suggested solutions, the spring is constantly connected to the pads as the wear varies, i.e. according to the variation of the distance between the two pads 6, and therefore of the distance between the two portions of the spring attachment to the pads. It is also ensured that the forces applied by the spring on the plate are only axial (perpendicular to the plane of symmetry in the figures indicated with reference numeral 16) and that no torques are applied which could cause the rotation of the plate itself. The spring system on the plate is configured as a hinge.
[0005] Furthermore, the inclinations of the spring arms are such that the spring is parallel to the surface of the disc under maximum wear conditions, thus avoiding contact of the spring with the disc.
[0006] The shape of the second connection 24 ensures that the spring can be taken to the maximum wear condition with the sliding connection sections on the inner upper edge and the upper surface of the plate coupling seat.
[0007] By virtue of the hook 23, the spring is prevented from slipping out of the caliper in a radial direction (parallel to the symmetry axis 16) under the condition of maximum wear of the pads. Flowever, this hook does not work to attach the plate externally, remaining facing the lower edge of the plate itself and mostly not in contact under conditions of normal use.
[0008] DRAWINGS
[0009] In order to better understand the invention and appreciate the advantages thereof, some non-limiting exemplary embodiments will be described below with reference to the accompanying drawings, in which:
[0010] - figure 1 is a perspective view of a disc brake according to an embodiment of the invention;
[0011] - figure 2 is a further perspective view of the disc brake in figure 1 ; [0012] - figure 3 is a radial section view (with respect to a rotation axis of a disc brake) of the disc brake in figure 1 under non-worn pad condition,
[0013] - figure 4 is a further radial section view of the disc brake in figure 1 , under worn pad condition;
[0014] - figure 5 is a cross-section view (with respect to a rotation axis of a disc brake) of the disc brake in figure 1 ;
[0015] - figure 6 is a front view of a pad of the disc brake in figure 1 ;
[0016] - figure 7 is a perspective view of the pad in figure 6;
[0017] - figure 8 is a front view of a spring of the disc brake in figure 1 ;
[0018] - figure 9 is a perspective view of the spring in figure 8;
[0019] - figure 10 shows a perspective side of a brake caliper according to a further embodiment;
[0020] - figure 1 1 is an axonometric view of a detail of an assembly of pads facing each other and an interposed spring associated therewith;
[0021] - figure 12 is a front view of a detail of a brake pad according to a different embodiment, in which the detail of the coupling position of the brake pad to the spring is highlighted;
[0022] - figure 13 is a top view of the detail in figure 12;
[0023] - figure 14 shows an axonometric view of a spring according to a further embodiment;
[0024] - figure 15 is a front view of the spring in figure 14;
[0025] - figures from 16 to 18 diagrammatically show from the circumferential direction an assembly of two pads biased by a spring and facing a brake disc under three different conditions of wear of the pad friction material;
[0026] - figures from 19 to 22 diagrammatically show a spring connected to a plate coupling portion in which four different pad positions are illustrated, as a function of four different conditions of wear of the friction material not shown, to highlight the actions which are exchanged by the spring to the plate coupling portion;
[0027] - figure 23 diagrammatically shows a spring associated with two opposite plate coupling portions, in which the actions of the spring are broken down in radial and axial directions to show how the radial actions substantially compensate each other and the resulting are axial actions which constantly and elastically bias the pads as they move away from the disc.
[0028] DETAILED DESCRIPTION OF SOME EMBODIMENTS OF THE INVENTION [0029] With reference to the figures, a disc brake, in particular for use on motor vehicles, is globally indicated by reference numeral 1 . In the specific case, it is a disc brake of the floating caliper type. However, the invention is also applicable to brakes with fixed calipers.
[0030] The disc brake 1 comprises a caliper 2 and a brake disc 3, in which the brake disc 3 defines a rotation axis 10. The caliper 2 is arranged straddling the brake disc 3 and can be fixed to a bracket 4 by means of a sliding support (e.g. fig. 1 -2).
[0031] The bracket 4 is fixed to a vehicle suspension, while the brake disc 3, provided with an annular braking band 5, can be connected to the wheel hub of the vehicle (not shown).
[0032] The brake disc 1 comprises an assembly 100, wherein the assembly 100 comprises at least two pads 6 having a support plate 7 and a friction material coating 8, each of said at least two pads 6 is adapted to be accommodated in an appropriate pocket
9 of a caliper 2 so that each of said at least two pads 6 can be positioned on a side of a brake disc 3 of a disc brake 5 (e.g. fig. 3-5).
[0033] The pads 6 can be displaced mainly in axial direction (parallel to the rotation axis
10 of the brake disc 3) towards the brake disc 3 by means of thrust means, e.g. such as one or more hydraulic cylinder-piston units 1 1 arranged in the caliper 2, so as to clamp, via the friction material 8, a sector of the braking band 5, the surface and shape of which corresponds to those of the friction lining 8.
[0034] The support plate 7 of the pads 6 has a substantially rectangular shape and forms two ears 12 protruding outwards from the support plate 7.
[0035] Each one of the two ears 12 forms an abutment wall 14 adapted to be inserted in the pockets 9 of the caliper 2. Advantageously, the abutment wall 14” has an angular shape, forming a first abutment wall 14’ and a second abutment wall 14’ adapted to abut against a plate mounted on two different surfaces of a pocket 9 of the caliper 2 (e.g. fig. 5-7).
[0036] Furthermore, each of the ears 12 forms a coupling seat 13.
[0037] Furthermore, the assembly 100 further comprises at least one spring 15 shaped to be positioned straddling the brake disc 3, and which applies an elastic preload on the pads 6 so as to bias the pads 6 elastically away from the brake disc 3.
[0038] The at least one spring 15 may perform the further function of stopping the pads 6 elastically in the pockets 9 so as to reduce the onset of vibrations and noise due to movements of the pads with respect to the caliper 2.
[0039] According to an aspect of the invention, the spring 15 is configured so as to be directly connected only to the pads 6 (fig. 3-5). Therefore, the spring 15 is not constrained by any other disc brake component 1 except for the pads 6.
[0040] Advantageously, such a configuration increases the assembly flexibility of the at least one spring 15 to the disc brake 1 because the at least one spring 15 is connected exclusively to the pads 6, and thus may be implemented indifferently to various disc brakes 1 and various calipers 2, with no need to adapt such disc brakes 1 or such calipers 2 to the spring 15 or vice versa.
[0041] With further advantage, such a configuration of the spring 15 is space-saving, because it makes up for the formation on the caliper 2 of a specific connection portion for the spring 15.
[0042] According to a further aspect of the invention, two springs 15 are arranged straddling the brake disc 3, so as to apply an elastic preload on the pads 6.
[0043] Specifically, each of the two springs 15 is connected to the ear 12 of a first pad 6 and to the corresponding opposite ear 12 of the other pad 6, respectively.
[0044] According to an embodiment of the invention, at least one spring 15 is substantially shaped as an inverted“U” (fig. 8-9).
[0045] The at least one spring 15 defines a symmetry plane 16 (geometric, not material) which is transverse to the rotation axis 10 of the brake disc 3 when at least one spring 15 is mounted in the operating position.
[0046] The at least one spring 15 consists of two coupling portions or spring arms 17 and of a bridge portion 18 interposed between the two coupling portions or spring arms 17.
[0047] The two coupling portions or spring arms 17 are configured to couple to a respective ear 12 of the two pads 6 and said two coupling portions or spring arms 17 are symmetrical with respect to the symmetry plane 16.
[0048] According to this embodiment, the spring 15 is deformed elastically (in particular, by accumulating elastic energy) by a relative movement of the coupling portions or spring arms 17, moved by the respective pads 6, with respect to the bridge portion 18.
[0049] According to an embodiment, each of the two coupling portions or spring arms 17 is connected to the bridge portion 18 by means of a first connector 19, wherein the first connector 19 is shaped as a loop or arc of circumference.
[0050] Advantageously, such a shape of the first connector 19 ensures that the elastic return force of the spring 15 (caused by the elastic deformation of the spring 15 by the action of the pads 6) is incremental as the wear of the pads 6 varies, i.e. as the distance between the two coupling pads 6 (and therefore the distance between the two coupling portions or spring arms 17 attached to the pads 6).
[0051] According to an embodiment, each of the coupling portions or spring arms 17 of the spring 15 is substantially“Z”-shaped.
[0052] In particular, each of the coupling portions or spring arms 17 consists of a first diagonal portion 21” and a second diagonal portion 21”, which are substantially parallel to each other, between which a return portion 22, which is substantially transversal to the two diagonal portions 21”, 21”, is interposed.
[0053] The return portion 22 is configured so as to lie on a respective coupling seat 13 of the ears 12.
[0054] Advantageously, such configuration of the return portion 22 guarantees that the spring 15 is constantly connected to the pads 6 when the wear of the pads 6 varies, i.e. with the distance between the two pads 6 (and therefore the distance between the two coupling portions or spring arms 17 coupled to the pads 6), and in particular when the pads 6 are new and the spring is very open (fig. 3-4).
[0055] According to a further embodiment, the first diagonal portion 2T of each of the coupling portions or spring arms 17 is connected at a first end thereof to the return portion 22 by means of a second connector 24, wherein the second connector 24 is shaped as a loop or arc of circumference.
[0056] Advantageously, such a shape of the second connector 24 further ensures that the elastic return force of the spring 15 (caused by the elastic deformation of the spring 15 by the action of the pads 6) is incremental as the wear of the pads 6 varies, i.e. with the distance between the two coupling pads 6 (and therefore the distance between the two coupling portions or spring arms 17 attached to the pads 6) when the disc brake 1 is not actuated.
[0057] According to an embodiment, a second end of the diagonal portion 2T forms a hook-shaped end portion 23.
[0058] Advantageously, such a hooked end portion 23 further guarantees a correct and stable connection of the spring 15 to the ears 12 of the pads 6.
[0059] According to an embodiment, the spring 15 is configured so that, in the working position, the coupling portions or spring arms 17 are interposed between the pads 6 and the brake disc 3.
[0060] According to an embodiment, the spring 15 is of the leaf type.
[0061] According to a further embodiment, the spring 15 is formed in a single strip shaped steel piece shaped so as to display only curvatures about axes which are substantially parallel to one another and substantially parallel to the symmetry plane 16 of the spring 15.
[0062] Advantageously, this simplifies the production process of spring 15, e.g. starting from sheet material, e.g. spring steel, which is sheared into strips and then bent and heat-treated to achieve its elastic return performance from said bent shape.
[0063] According to a further aspect of the invention, a caliper 2 comprises the assembly 100 described above.
[0064] According to an advantageous embodiment, the caliper 2 is of the“floating” type.
[0065] According to a further aspect of the invention, a disc brake 1 comprises the assembly 100 described above and the caliper 2 described above.
[0066] It is apparent that only some particular embodiments of the present invention have been described, to which those skilled in the art will be able to make all the changes required to adapt it to particular applications, without departing from the scope of protection of the present invention.
[0067] According to a general embodiment, an assembly 100 comprises at least two pads 6 having a support plate 7 and a friction material lining 8. Each of said at least two pads 6 is adapted to be accommodated in a pocket 9 of a caliper 2 so that each of said at least two pads 6 can be positioned on a side of a brake disc 3 of a disc brake 1 facing opposite braking surfaces 36.
[0068] Said brake disc 3 is a rotor adapted to rotate about a rotation axis 10 which defines an axial direction A-A, parallel to said rotation axis 10, a radial direction R-R, orthogonal to said rotation axis 10, and a circumferential direction C-C orthogonal to said axial A-A and radial R-R directions and a tangential direction T-T orthogonal to a radial R-R and circumferential C-C direction at their point of intersection.
[0069] Said assembly 100 further comprises at least one spring 15, shaped to be arranged straddling the disc brake 3.
[0070] Said spring 15 applies an elastic bias on the pads 6 so as to bias the pads 6 elastically away from the brake disc 3.
[0071] Said at least one spring 15 is configured to be directly connected only to the pads 6.
[0072] Said support plate 7 comprises at least one plate coupling portion 37.
[0073] In a section of said plate coupling portion 37 on a plane containing the axial direction A-A and the radial direction R-R, said plate coupling portion 37 comprises:
[0074] - an inner lower edge 25, adapted to face the brake disc 3 in the radially inward direction or towards the disc rotation axis 10;
[0075] - an inner upper edge 26, adapted to face the brake disc 3 in the radially outward direction or opposite to the disc rotation axis 10.
[0076] Said inner upper edge 26 continues on a direct upper surface 27 according to an axial direction A-A parallel to said disc rotation axis 10, thus forming an upper spring coupling plate portion edge 29.
[0077] Advantageously, said spring 15 is always in contact exclusively with:
[0078] - said inner lower edge 25
[0079] and
[0080] - said upper spring-coupling plate portion edge 29.
[0081] According to an embodiment, said spring 15 is a wire spring made in one piece.
[0082] According to an embodiment, said spring 15 is a wire spring having a circular cross-section.
[0083] According to an embodiment, said spring 15 is a wire spring made in one piece and said spring 15 is always in contact exclusively with a point or a line of said inner lower edge 25 and said upper spring-coupling plate portion edge 29.
[0084] According to an embodiment, said inner upper edge 26 is radially arranged on the side opposite to said inner lower edge 25.
[0085] Said inner upper edge 26 continues on a direct upper surface 27 according to an axial direction A-A parallel to said disc rotation axis 10.
[0086] Said upper surface 27 continues on an outer upper edge 28 adapted to be rotated in the opposite direction to the brake disc 3.
[0087] Said spring 15 is always in contact with said upper inner edge 26 or said upper surface 27 or said upper outer edge 28.
[0088] According to an embodiment, said spring 15 avoids resting on anything else but said at least two pads 6, thus avoiding the connection to said caliper 2 for relieving all or part of the elastic reaction thereon.
[0089] According to an embodiment, said assembly 100 comprises two springs 15 adapted to be arranged straddling the brake disc 3, so as to bias the pads 6 elastically and wherein both said two springs 15 are configured to be directly connected only to the pads 6.
[0090] According to an embodiment, said two springs 15 are disconnected at opposite sides of said two pads 6.
[0091] According to an embodiment, the support plate 7 of the pads 6 is substantially rectangular in shape, said support plate 7 forms two ears 12 which extend towards the outside of the support plate 7 in circumferential direction C-C. [0092] According to an embodiment, said at least one spring 15 cooperates with at least one of said ears 12.
[0093] According to an embodiment, each of the two ears 12 forms:
[0094] - an abutment wall 14, adapted to be abuttingly inserted into the pockets 9 of the caliper 2, wherein the abutment wall 14 is angular in shape, thus forming a first abutment wall 14’ and a second abutment wall 14” adapted to abut against metal sheets mounted to two different surfaces of a pocket 9 of the caliper 2; and
[0095] - a coupling seat 13.
[0096] According to an embodiment, each of the two springs 15 is connected to the ear 12 of a first pad 6 and to the ear 12 of the other pad 6, respectively, either directly or indirectly facing said first pad ear 12.
[0097] According to an embodiment, said at least one plate coupling portion 37 comprises said upper spring-coupling plate portion edge 29, one inner pad coupling portion side 30, adapted to face either directly or indirectly said brake disc 3, and a lower spring-coupling plate portion edge 30 comprising said inner lower edge 25 which continues on a lower surface 31 directed according to an axial direction A-A parallel to said disc rotation axis 10.
[0098] According to an embodiment, said upper spring-coupling plate portion edge 29 comprises an upper spring seat edge 32 shaped to fit intimately with a coupling portion or spring arms 17.
[0099] According to an embodiment, said lower spring-coupling plate portion edge 31 comprises a lower spring seat edge 34 shaped to fit intimately with a coupling portion or spring arms 17.
[00100] According to an embodiment, said inner pad coupling portion side 30 comprises an inner spring seat side 33 shaped to fit intimately with a coupling portion or spring arms 17.
[00101] According to an embodiment, the at least one spring 15 is substantially inverted“U”-shaped, and said at least one spring 15 defines a symmetry plane 16.
[00102] According to an embodiment, the at least one spring 15 comprises two coupling portions or spring arms 17 and of a bridge portion 18, said bridge portion 18 being interposed between the two coupling portions or spring arms 17.
[00103] According to an embodiment, said coupling portions or spring arms 17 are configured to be coupled to a respective ear 12 of the two pads 6.
[00104] According to an embodiment, said two coupling portions or spring arms 17 are symmetrical with respect to the symmetry plane 16. [00105] According to an embodiment, the spring 15 is elastically deformable by means of a relative movement of the coupling portions or spring arms 17, said coupling portions or spring arms 17 being movable by the respective pads 6, with respect to the bridge portion 18.
[00106] According to an embodiment, each of the two coupling portions or spring arms 17 is connected to the bridge portion 18 by means of a first connector 19, wherein said first connector 19 is shaped as a loop or arc of circumference.
[00107] According to an embodiment, said first connector 19 is spiral-shaped.
[00108] According to an embodiment, said first connection 19 is spiral-shaped with at least one first connection loop 35 forming an angle of at least 360 DEG.
[00109] According to an embodiment, each of the coupling portions or spring arms 17 of the spring 15 is substantially“Z”-shaped, and each of the coupling portions or spring arms 17 comprises:
[00110] - a first diagonal portion or first inclined portion 21
[00111] - a second diagonal portion or second inclined portion 21
[00112] - a return portion 22.
[00113] According to an embodiment, the first diagonal portion 21’ and the second diagonal portion 21” are substantially parallel to each other, and the return portion 22 is interposed between the first diagonal portion 21’ and the second diagonal portion 21”, said return portion being substantially transverse to the first diagonal portion 21’ and to the second diagonal portion 21”.
[00114] According to an embodiment, the return portion 22 is configured so as to lie on a respective coupling seat 13 of the ears 12.
[00115] According to an embodiment, the first diagonal portion 21’ of each of the coupling portions or spring arms 17 is connected at a first end thereof to the return portion 22 by means of a second connector 24, wherein the second connector 24 is shaped as a loop or arc of circumference.
[00116] According to an embodiment, a second end of the diagonal portion 21’ forms a hook-shaped end portion 23.
[00117] According to an embodiment, the spring 15 is configured so that, in the working position, the coupling portions or spring arms 17 are interposed between the pads 6 and the brake disc 3.
[00118] According to an embodiment, the spring 15 is of the wire type.
[00119] According to an embodiment, the spring 15 is a spring leaf. [00120] According to an embodiment, the spring 15 is formed in a single strip shaped steel piece shaped so as to display only curvatures about axes which are substantially parallel to one another and substantially parallel to the symmetry plane 16 of the spring 15.
[00121] The present invention further relates to a caliper 2 comprising an assembly 100, said assembly 100 comprising at least two pads 6 and at least one spring 15 according to any one of the embodiments described above.
[00122] According to an embodiment, the at least one spring 15 is configured to perform the further function of stopping the pads 6 elastically in the pockets 9 so as to reduce the onset of vibrations and noise due to movements of the pads with respect to the caliper 2.
[00123] According to an embodiment, said caliper body 2 is of the“floating” type.
[00124] The present invention further relates to a disc brake 1 comprising:
[00125] - an assembly 100 comprising at least two pads 6 and at least one spring
15 according to any one of the embodiments described above;
[00126] - a caliper 2; and
[00127] - a brake disc 3.
[00128] The present invention further relates to a method for biasing two facing brake pads 6 constantly and elastically by means of a spring 15, wherein there are provided the steps of:
[00129] - providing an assembly according to any one of the embodiments described above; and
[00130] - during wear of the friction material 8 of the pads 6, rotating the spring 15 like a hinge about the spring-coupling plate portion 37, sliding the spring 15 against said inner lower edge 25 and said upper spring-coupling plate portion edge 29 to apply an elastic bias for distancing the pads 6 from the brake, when the braking action ceases, substantially globally directed in the axial direction A-A.
LIST OF REFERENCE SYMBOLS . Disc brake
. Caliper
. Brake disc
. Bracket
. Braking band
. Pads
. Support plate
. Friction material
. Pockets
0. Rotation axis (of the brake disc)
1. Hydraulic cylinder-piston
2. Ears (of the pads)
3. Coupling seats
4. Abutment wall
4’. First abutment wall
4”. Second abutment wall
5. Spring
6. Symmetry plane (of the spring)
7. Coupling portion or spring arm
8. Bridge portion
9. First connector
T. First diagonal portion or first inclined portion
1”. Second diagonal portion or second inclined portion2. Return portion
3. Hook-shaped end portion
4. Second connector 25. Inner lower edge
26. Inner upper edge
27. Upper surface
28. Outer upper edge
29. Upper edge of plate coupling portion to the spring
30. Inner pad coupling portion side
31. Lower spring-coupling plate portion edge
32. Upper edge spring seat
33. Inner side spring seat
34. Lower edge spring seat
35. First connection loop
36. Disc brake braking surfaces
37. Plate coupling portion to the spring
100. Pad-spring assembly
A-A axial direction
R-R radial direction
C-C circumferential direction
T-T tangential direction

Claims

1. An assembly (100) comprising:
- at least two pads (6) having a support plate (7) and a friction material coating (8), each of said at least two pads (6) being adapted to be accommodated in a pocket (9) of a caliper (2) so that each of said at least two pads (6) can be positioned on a side of a brake disc (3) of a disc brake (1 ) facing opposite braking surfaces (36);
said brake disc (3) being a rotor adapted to rotate about a rotation axis (10) which defines an axial direction (A-A), parallel to said rotation axis (10), a radial direction (R-R), orthogonal to said rotation axis (10), and a circumferential direction (C-C) orthogonal to said axial (A-A) and radial (R-R) directions and a tangential direction (T-T) duly orthogonal to a radial (R-R) and circumferential (C-C) direction at their point of intersection;
- at least one spring (15), shaped to be arranged straddling the disc brake (3), wherein said spring (15) applies an elastic bias on the pads (6) so as to bias the pads (6) elastically away from the brake disc (3);
wherein said at least one spring (15) is configured to be directly connected only to the pads (6);
said support plate (7) comprising at least one plate coupling portion (37),
wherein, in a section of said plate coupling portion (37) on a plane containing the axial direction (A-A) and the radial direction (R-R), said plate coupling portion (37) comprises:
- an inner lower edge (25), adapted to face the brake disc (3) in the radially inward direction or towards the disc rotation axis (10);
- an inner upper edge (26), adapted to face the brake disc (3) in the radially outward direction or opposite to the disc rotation axis (10);
- said inner upper edge (26) continues on a direct upper surface (27) according to an axial direction (A-A) parallel to said disc rotation axis (10), thus forming an upper spring-coupling plate portion edge (29);
and wherein said spring (15) is always in contact exclusively with:
- said inner lower edge (25)
and - said upper spring-coupling plate portion edge (29).
2. An assembly (100) according to claim 1 , wherein said spring (15) is a wire spring made in one piece;
or
wherein said spring (15) is a wire spring having a circular cross-section;
and/or wherein
said spring (15) is a spring in one piece;
wherein said spring (15) is always in contact exclusively with a point or a line of said inner lower edge (25) and said upper spring-coupling plate portion edge (29).
3. An assembly (100) according to claim 1 or 2, wherein said inner upper edge (26) is radially arranged on the side opposite to said inner lower edge (25) and wherein said inner upper edge (26) continues on a direct upper surface (27) according to an axial direction (A- A) parallel to said disc rotation axis (10); and wherein
said upper surface (27) continues on an outer upper edge (28) adapted to be rotated in the opposite direction to the brake disc (3); and wherein
said spring (15) is always in contact with said upper inner edge (26) or said upper surface (27) or said upper outer edge (28).
4. An assembly (100) according to any one of the preceding claims, wherein:
said spring (15) avoids resting on anything else but said at least two pads (6), thus avoiding the connection to said caliper (2) for relieving all or part of the elastic reaction thereon;
and/or wherein
said assembly (100) comprises two springs (15) adapted to be arranged straddling the brake disc (3), in order to bias the pads (6) elastically and wherein both said two springs (15) are configured to be directly connected only to the pads (6);
and/or wherein said two springs (15) are disconnected at opposite sides of said two pads (6).
5. An assembly (100) according to any one of the preceding claims, wherein the support plate (7) of the pads (6) is substantially rectangular in shape, said support plate (7) forms two ears (12) which extend towards the outside of the support plate (7) in circumferential direction (C-C);
and/or wherein
said at least one spring (15) cooperates with at least one of said ears (12).
6. An assembly (100) according to claim 5, wherein each of the two ears (12) forms:
- an abutment wall (14), adapted to be abuttingly inserted into the pockets (9) of the caliper (2), wherein the abutment wall (14) has is angular in shape, thus forming a first abutment wall (14’) and a second abutment wall (14”) adapted to abut against metal sheets mounted to two different surfaces of a pocket (9) of the caliper (2); and
- a coupling seat (13);
and/or wherein
each of the two springs (15) is connected to the ear (12) of a first pad (6) and to the ear (12) of the other pad (6), respectively, either directly or indirectly facing said first pad ear (12).
7. An assembly (100) according to any one of the preceding claims, wherein said at least one plate coupling portion (37) comprises said upper spring-coupling plate portion edge (29), one inner pad coupling portion side (30), adapted to face either directly or indirectly said brake disc (3), and a lower spring-coupling plate portion edge (30) comprising said inner lower edge (25) which continues on a lower surface (31 ) directed according to an axial direction (A-A) parallel to said disc rotation axis (10);
and/or wherein
said upper spring-coupling plate portion edge (29) comprises an upper spring seat edge (32) shaped to fit intimately with a coupling portion or spring arm (17);
and/or wherein said lower spring-coupling plate portion edge (31 ) comprises a lower spring seat edge (34) shaped to fit intimately with a coupling portion or spring arm (17);
and/or wherein
said inner pad coupling portion side (30) comprises an inner spring seat side (33) shaped to fit intimately with a coupling portion or spring arm (17).
8. An assembly (100) according to any one of the preceding claims, wherein the at least one spring (15) is substantially inverted“U”-shaped, and said at least one spring (15) defines a symmetry plane (16);
and/or wherein
the at least one spring (15) comprises two coupling portions or spring arms (17) and of a bridge portion (18), said bridge portion (18) being interposed between the two coupling portions or spring arms (17),
and/or wherein said coupling portions or spring arms (17) are configured to be coupled to a respective ear (12) of the two pads (6),
and/or wherein said two coupling portions or spring arms (17) are symmetrical with respect to the symmetry plane (16);
and/or wherein
the spring (15) is elastically deformable by means of a relative movement of the coupling portions or spring arms (17), said coupling portions or spring arms (17) being movable by the respective pads (6), with respect to the bridge portion (18);
and/or wherein
each of the two coupling portions or spring arms (17) is connected to the bridge portion (18) by means of a first connector (19), wherein said first connector (19) is shaped as a loop or arc of circumference;
and/or wherein said first connection (19) is spiral-shaped;
and/or wherein said first connection (19) is spiral-shaped with at least one first connection loop (35) forming an angle of at least 360 DEG;
and/or wherein
each of the coupling portions or spring arms (17) of the spring (15) is substantially“Z”- shaped, and each of the coupling portions or spring arms (17) comprises:
- a first diagonal portion or first inclined portion (21’);
- a second diagonal portion or second inclined portion (21”);
- a return portion (22);
and/or wherein the first diagonal portion (21’) and the second diagonal portion (21”) are substantially parallel to each other, and
the return portion (22) is interposed between the first diagonal portion (21’) and the second diagonal portion (21”), said return portion being substantially transverse to the first diagonal portion (21’) and to the second diagonal portion (21”).
9. An assembly (100) according to claim 8, wherein the return portion (22) is configured so as to lie on a respective coupling seat (13) of the ears (12);
and/or wherein
the first diagonal portion (21’) of each of the coupling portions or spring arms (17) is connected at a first end thereof to the return portion (22) by means of a second connector (24), wherein the second connector (24) is shaped as a loop or arc of circumference; and/or wherein
a second end of the diagonal portion (21’) forms a hook-shaped end portion (23);
and/or wherein
the spring (15) is configured so that, in the working position, the coupling portions or spring arms (17) are interposed between the pads (6) and the brake disc (3);
and/or wherein
the spring (15) is of the wire type;
and/or wherein
the spring (15) is of the leaf type;
and/or wherein
the spring (15) is formed in a single strip-shaped steel piece shaped so as to display only curvatures about axes which are substantially parallel to one another and substantially parallel to the symmetry plane (16) of the spring (15).
10. A caliper (2) comprising an assembly (100), said assembly (100) comprising at least two pads (6) and at least one spring (15) according to any one of the preceding claims.
11. A caliper (2) according to claim 10, wherein the at least one spring (15) is configured to perform the further function of stopping the pads (6) elastically in the pockets (9) so as to reduce the onset of vibrations and noise due to movements of the pads with respect to the caliper (2).
12. A caliper (2) according to claim 10 or 1 1 , wherein the caliper (2) is of the“floating” type.
13. A disc brake (1 ) comprising:
- an assembly (100) comprising at least two pads (6) and at least one spring (15) according to one of the claims from 1 to 9;
- a caliper (2) according to one of the claims from 10 to 12; and
- a brake disc (3).
14. A method for constantly and elastically biasing two facing brake pads (6) by means of a spring (15), wherein there are provided the steps of:
- providing an assembly according to at least one of the claims from 1 to 9;
- connecting said at least one spring (15) directly and exclusively to the pads (6);
- during the wear of the friction material (8) of the pads (6), rotating the spring (15) like a hinge about the spring-coupling plate portion (37), sliding the spring (15) against said inner lower edge (25) and said upper spring-coupling plate portion edge (29) to apply an elastic bias distancing the pads (6) away from the brake, when the braking action ceases, substantially globally directed in the axial direction (A-A).
PCT/IB2019/061201 2018-12-20 2019-12-20 Assembly of at least two brake pads and at least one spring WO2020129012A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US17/416,062 US11852207B2 (en) 2018-12-20 2019-12-20 Assembly of at least two brake pads and at least one spring
EP19836587.6A EP3899306A1 (en) 2018-12-20 2019-12-20 Assembly of at least two brake pads and at least one spring
CN201980084775.2A CN113195920B (en) 2018-12-20 2019-12-20 Assembly of at least two brake pads and at least one spring
JP2021536008A JP2022515189A (en) 2018-12-20 2019-12-20 Assembly of at least two brake pads and at least one spring

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
IT102018000020527A IT201800020527A1 (en) 2018-12-20 2018-12-20 ASSEMBLY OF PADS-SPRING FOR DISC BRAKE
IT102018000020527 2018-12-20
IT102019000023940A IT201900023940A1 (en) 2019-12-13 2019-12-13 Assembly of at least two brake pads and at least one spring
IT102019000023940 2019-12-13

Publications (1)

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WO2020129012A1 true WO2020129012A1 (en) 2020-06-25

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EP (1) EP3899306A1 (en)
JP (1) JP2022515189A (en)
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CN113195920A (en) 2021-07-30
EP3899306A1 (en) 2021-10-27
JP2022515189A (en) 2022-02-17
US11852207B2 (en) 2023-12-26
US20220056970A1 (en) 2022-02-24

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